Valve assembly

ABSTRACT

A rotary valve is disclosed. The valve comprises a drive shaft, a rotor coupled to the drive shaft, a least one bearing surface coupled to the rotor, a stator adjacent to the rotor, at least one solid bearing surface coupled to the stator, and at least one ring bearing surface coupled to the stator.

REFERENCE TO RELATED APPLICATIONS

This application is a continuation of U.S. Non-Provisional applicationSer. No. 13/940,487, filed Jul. 12, 2013, entitled “Valve Assembly,”which claims priority to U.S. Provisional Application No. 61/670,687,filed Jul. 12, 2012, entitled “Valve Assembly,” both of which are herebyspecifically and entirely incorporated by reference.

BACKGROUND

1. Field of the Invention

The invention is directed to valves, specifically, the invention isdirected to rotary valves.

2. Background of the Invention

Rotary valves are used in industry for a number of applications likecontrolling the flow of liquids to molds, regulating the flow ofhydraulic fluids to control various machine functions, industrialprocess control, and controlling fluids which are directed against workpieces. The vast majority of these applications are conducted at lowfluid pressures and at either low rotational speeds or through anindexed movement. These applications have been addressed throughapplication of various known fluid regulation valve applicationsincluding gate valves, ball valves, butterfly valves, rotating shaftswith various void designs and configurations, solenoid actuated valvesof various designs, and valves designed with disks with multiple holesto redirect flow streams. These applications are generally acceptablefor low speed, low pressure processes, but are not suitable for highspeed, high pressure processes.

For example, solenoid valves are effective for regulating fluid flow upto a frequency of approximately 300 Hz at a pressure of up to 200 psi.These limitations are primarily due to the physical design of thesolenoid which relies upon the reciprocating motion of magnetic contactsand is therefore subject to significant acceleration and decelerationforces, particularly at higher frequencies. These forces, the resultingjarring action, and the frictional heat generated make these type valvessubject to failure at high frequencies of actuation.

Rotary valves employing multiple outlets have been used at frequenciesup to 1000 Hz in applications where a low pressure differential betweenvalve inlet and outlet ports is desired. These valves, however, arelarge and complex and necessarily have significant physical spacerequirements for the valve and for the appurtenant inlet and outletpiping.

Other types of valves have disadvantages that include: the valveactuation cycle speed (frequency) of the valve is too low, the valve islarge and physically complex, the valve creates significant head loss,the valve cannot satisfactorily operate at high inlet pressures, or thevalve cannot create the necessary frequency or amplitude of flowperturbation.

For the foregoing reasons, there is a need for a high-speed, highpressure rotary valve for controlling the flow of a fluid to producehigh frequency fluid pulses or perturbations. Further, there is a needfor such a valve which is relatively simple in design, compatible withstandardized piping systems, and suitable for high pressure applicationswith minimal head loss through the valve.

SUMMARY OF THE INVENTION

The present invention overcomes the problems and disadvantagesassociated with current strategies and designs and provides new toolsand methods creating rotary valves.

One embodiment of the invention is directed to a rotary valve. The valvecomprises a drive shaft, a rotor coupled to the drive shaft, a least onebearing surface coupled to the rotor, a stator adjacent to the rotor, atleast one solid bearing surface coupled to the stator and at least onering bearing surface coupled to the stator.

Preferably, during rotation, the at least one bearing surface coupled tothe rotor slides across the at least one solid bearing surface and theat least one ring bearing surface. In the preferred embodiment the atleast one bearing surface coupled to the rotor, the at least one solidbearing surface, and the at least one ring bearing surface arepositioned at an equal distance from a rotational axis of the driveshaft. Preferably the at least one ring bearing surface is adapted toallow fluid to flow therethrough. Preferably the at least one bearingsurface coupled to the rotor, the at least one solid bearing surface,and the at least one ring bearing surface are polycrystalline diamondcompacts.

In the preferred embodiment, the at least one bearing surface coupled tothe rotor and the at least one ring bearing surface form a seal betweenthemselves when aligned. Preferably, the drive shaft is powered by fluidflowing through the rotary valve. Preferably, there are an equal numberof bearing surfaces coupled to the rotor and ring bearing surfaces.Preferably, the rotor comprises at least two arms and the at least twoarms are rotationally balanced. In the preferred embodiment, fluidpassing through the rotary valve forces the rotor into contact with thestator.

Other embodiments and advantages of the invention are set forth in partin the description, which follows, and in part, may be obvious from thisdescription, or may be learned from the practice of the invention.

DESCRIPTION OF THE DRAWING

The invention is described in greater detail by way of example only andwith reference to the attached drawing, in which:

FIG. 1 is an isometric view of a rotary valve embodiment of theinvention.

FIG. 2 is a view of an embodiment of the valve of the invention in theopen position.

FIG. 3 is a view of an embodiment of the valve of the invention in theclosed position.

FIG. 4 is side view of an embodiment of the valve of the inventiondepicting the fluid pressure maintaining the valve seat.

DESCRIPTION OF THE INVENTION

As embodied and broadly described herein, the disclosures herein providedetailed embodiments of the invention. However, the disclosedembodiments are merely exemplary of the invention that may be embodiedin various and alternative forms. Therefore, there is no intent thatspecific structural and functional details should be limiting, butrather the intention is that they provide a basis for the claims and asa representative basis for teaching one skilled in the art to variouslyemploy the present invention

A problem in the art capable of being solved by the embodiments of thepresent invention is creating a high pressure, wear resistant rotaryvalve. It has been surprisingly discovered that by using low-frictionstators and rotors, a rotary valve can be constructed that is wearresistant, capable of sealing at high pressures, can open and close athigh speeds, and is unaffected by abrasive fluids.

FIG. 1 depicts an embodiment of a rotary valve 100. Rotary valve 100preferably comprises a drive shaft 105, a rotor 110 and a stator 115. Inthe preferred embodiment, drive shaft 105, rotor 110, and stator 115 areall made of the same corrosive resistant material, however eachcomponent can be of a different material, or combinations thereof. Forexample, drive shaft 105, rotor 110, and stator 115 can be made ofsteel, carbon steel, steel alloys, bronze, brass, copper, titanium,aluminum, aluminum alloys, plastics, combinations thereof, or othermaterials.

In the preferred embodiment drive shaft 105 and rotor 110 arerotationally coupled and rotate at the same rate, while stator 115remains stationary. However, drive shaft 105 and stator 115 can berotationally coupled while rotor 110 remains stationary. Drive shaft 105is preferably coupled to a rotational force generator. The rotationalforce generator can be, for example, an electric, gas, or steam motor,an inductor, a turbine (e.g. a fluid turbine powered by liquid or gas),a hand crank, or another method of imparting rotational force to rotor110. In the preferred embodiment, drive shaft 105 can rotate at speedsbetween 800 and 1200 rpm.

Preferably, rotor 110 extends, symmetrically from the center of driveshaft 105. Preferably, to keep the system in balance during rotation,the arms of rotor 110 extend in diametrically opposed directions fromthe center of drive shaft 105. While two arms are depicted in thefigures, rotor 110 can have three, four, five, or another number ofarms, or rotor 110 can be a disk or have another shape. Rotor 110preferably has at least one solid bearing surface 120 coupled to eacharm. As shown in the figures, each arm has two solid bearing surfaces120, however another number of bearing surfaces 120 can be used. Bearingsurfaces 120 extend from rotor 110 toward stator 115. In the preferredembodiment each bearing surface 120 is a polycrystalline diamond compact(PDC). However, each bearing surface 120 can be aluminum oxide, siliconcarbide, cubic boron nitride, or another erosion and abrasion resistantmaterial. Each bearing surface 120 is preferably 2 inches in diameterand all of the bearing surfaces 120 are preferably identical.

Stator 115 is preferably a disk with a plurality of bearing surfaces 125projecting towards rotor 110, however stator 115 can have another shape.Stator 115 is preferably coaxial with drive shaft 105, however stator115 can have a different axial arrangement. Preferably, stator 115 has adiameter equal to the inner diameter of a device into which valve 100 isplaced. For example, if valve 100 is used in a drill string fordown-hole drilling, the diameter of stator 115 would be equal to theinner diameter of the body of the drill string. Having the diameter ofstator 115 equal to the inner diameter of the device into which valve100 is placed, insures that all of the fluid passes through valve 100.

Stator 115 has two types of bearing surfaces 125, ring bearing surfaces125 a and solid bearing surfaces 125 b. In the preferred embodiment bothring bearing surfaces 125 a and solid bearing surfaces 125 b are made ofthe same material. Preferably, bearing surfaces 125 are made of PDC.However, other erosion and abrasion resistant materials can be used, forexample aluminum oxide, silicon carbide, or cubic boron nitride.Preferably ring bearing surfaces 125 a are identical to sold bearingsurfaces 125 b, however ring bearing surfaces 125 a have their centersbored out. For example, the centers can be bored out using an electricaldischarge machine (EDM). The holes (or nozzles) in the center of ringbearing surface 125 a can be 1 inch in diameter, 1.25 inches indiameter, or another diameter depending on the demands of the fluidspassing through the valve. Ring bearing surface 125 a have the duelfunction of allowing fluid to pass through the valve and acting as abearing surface between stator 115 and rotor 110. The figures showstator 115 having four solid bearing surfaces 125 b and four ringbearing surfaces 125 a. Another number of solid and ring bearingsurfaces can be used as long as there is at least one ring bearingsurface 125 a. The ring bearing surface allows fluid to pass throughvalve 100.

In the preferred embodiment each bearing surface 120 and bearing surface125 is positioned at the same distance from the axis of rotation of thedrive shaft 105 so that the bearing surfaces 120 pass over the bearingsurfaces 125 when the rotor 110 rotates. Preferably, there is an equalnumber of bearing surfaces 120 and ring bearing surfaces 125 a, howeverthere can be more or less bearing surfaces 120 than ring bearingsurfaces 125 a.

As drive shaft 105 and rotor 110 rotate, bearing surfaces 120 moveacross bearing surfaces 125. During rotation, valve 100 moves from anopen position (shown in FIG. 2), through intermediary positions, to aclosed position (shown in FIG. 3). Preferably, when valve 100 is in theopen position, fluid is able to pass through ring bearing surfaces 125a. When valve 100 is in the closed position, preferably bearing surfaces120 create a seal with ring bearings surfaces 125 a and do not allowfluid to pass through valve 100. In the embodiment show in the figures,at certain rotational positions, two of the ring bearing surfaces 125 aare covered while two of the ring bearing surfaces 125 a are uncovered.However, in other embodiments, where it is undesirable to have asemi-open position, the bearing surfaces can be arranged so that thereis no rotational position where a portion of the ring bearing surfaces125 a are uncovered. Additionally, the bearing surfaces can be arrangedsuch that there is always at least one ring bearing surface 125 a thatis uncovered. Additionally, bearing surfaces 120 can also be ringbearing surfaces such that the open position for valve 100 is when thering bearing surfaces of rotor 110 and stator 115 align and the closedposition for valve 100 is when the bearing surface of rotor 110 isaligned with the solid bearing surfaces of stator 115.

In the preferred embodiment, rotor 110 is forced against stator 115 bythe pressure of the fluid flowing through valve 100 (as shown in FIG.4). The pressure of the fluid preferably maintains the valve seat,providing the necessary seals between bearing surface 120 and ringbearing surface 125 a. In other embodiments, stator 100 is coupled torotor 110. For example, stator 100 can be coupled to rotor 110 by abolt, a bearing, friction, a cotter pin, or another fastener.

Other embodiments and uses of the invention will be apparent to thoseskilled in the art from consideration of the specification and practiceof the invention disclosed herein. All references cited herein,including all publications, U.S. and foreign patents and patentapplications, are specifically and entirely incorporated by reference.It is intended that the specification and examples be consideredexemplary only with the true scope and spirit of the invention indicatedby the following claims. Furthermore, the term “comprising of” includesthe terms “consisting of” and “consisting essentially of.”

The invention claimed is:
 1. A rotary valve, comprising: a drive shaft;a rotor coupled to the drive shaft and having a rotor surface; at leastone solid bearing surface coupled to the rotor, extending from the rotorsurface, and adapted to rotate about the drive shaft; a stator adjacentto the rotor and having a stator surface, wherein the stator surfacefaces the rotor surface; at least one solid bearing surface coupled tothe stator and extending from the stator surface toward the rotorsurface; and at least one ring bearing surface coupled to the stator andextending from the stator surface toward the rotor surface; wherein therotor comprises at least two arms and the at least two arms arerotationally balanced.
 2. The rotary valve of claim 1, wherein, duringrotation, the at least one solid bearing surface coupled to the rotorslides across the at least one solid bearing surface coupled to thestator and the at least one ring bearing surface.
 3. The rotary valve ofclaim 1, wherein the at least one solid bearing surface coupled to therotor, the at least one solid bearing surface, and the at least one ringbearing surface coupled to the stator are positioned at an equaldistance from a rotational axis of the drive shaft.
 4. The rotary valveof claim 1, wherein the at least one ring bearing surface is adapted toallow fluid to flow therethrough.
 5. The rotary valve of claim 1,wherein the at least one solid bearing surface coupled to the rotor, theat least one solid bearing surface coupled to the stator, and the atleast one ring bearing surface are polycrystalline diamond compacts. 6.The rotary valve of claim 1, wherein the at least one solid bearingsurface coupled to the rotor and the at least one ring bearing surfaceform a seal between themselves when aligned.
 7. The rotary valve ofclaim 1, wherein the drive shaft is powered by fluid flowing through therotary valve.
 8. The rotary valve of claim 1, wherein there are an equalnumber of solid bearing surfaces coupled to the rotor and ring bearingsurfaces.
 9. The rotary valve of claim 1, wherein fluid passing throughthe rotary valve forces the rotor into contact with the stator.
 10. Therotary valve of claim 1, wherein a bore in the ring bearing surface isparallel to the drive shaft.
 11. The rotary valve of claim 1, whereinthe rotor and stator are coaxial.